EP1666753B1 - Hydraulic cylinder, especially throw-out cylinder for hydraulic clutch actuation in vehicles - Google Patents

Description

TECHNICAL AREA

The invention relates to a hydraulic cylinder according to the preamble of claim 1. In particular, the invention relates to a slave cylinder for a hydraulic clutch actuation for motor vehicles, as they are used in masses in the automotive industry.

STATE OF THE ART

A conventional hydraulic clutch actuation for motor vehicles eg GB 1 223 333 has a master cylinder connected to a reservoir filled with hydraulic fluid. The master cylinder has a cylinder housing, in the housing bore a piston is received longitudinally displaceable. The master cylinder piston bounded in the housing bore of the cylinder housing a pressure chamber and can be mechanically acted upon by means of a clutch pedal or an electric motor drive with an actuating force. The pressure chamber of the master cylinder is hydraulically connected via a pressure line to a pressure chamber of a slave cylinder, so that the pressure generated by depressing the clutch pedal or electromotive displacement of the master cylinder piston in the pressure chamber of the master cylinder via the liquid column in the pressure line to the pressure chamber of the slave cylinder is transferable. The slave cylinder also has a cylinder housing with a housing bore in which a pressure chamber of the slave cylinder limiting and thus acted upon by the pressure generated in the master cylinder piston is taken longitudinally displaceable. The slave cylinder piston is associated with a piston rod which acts on a clutch lever, which in turn with the release bearing of the clutch in operative connection stands. As a result, the release bearing of the clutch via the slave cylinder piston can be acted upon by an actuating force to separate via a release mechanism, the clutch pressure plate from the Kupplungsmitnehmerscheibe and thus the engine from the transmission of the motor vehicle.

A generic slave cylinder for a hydraulic clutch actuation for motor vehicles is from the DE 43 22 969 A1 known. This slave cylinder has a pressure chamber which is delimited on one side by a piston which is received longitudinally displaceably in a cylinder housing. On the other hand, the pressure space of a housing bottom of the cylinder housing is limited, and radially outward from a peripheral wall of the cylinder housing, which is formed by an inserted in a housing base tube part. In order to move the piston in the cylinder housing, the pressure chamber can optionally be acted upon via a provided on the housing bottom pressure port with a pressure medium.

In this prior art, a further connection for a breather is also provided on the housing bottom, which serves to vent the slave cylinder after its assembly and filling with the pressure medium, ie dissipate any air bubbles or bubbles in the pressure medium to the outside. The breather port opens here near the central axis of the cylinder housing in the pressure chamber, which causes air that has accumulated or accumulated in the installed position of the slave cylinder at the top of the peripheral wall of the cylinder housing, is difficult to dissipate to the outside, especially one in the pressure chamber arranged helical compression spring for the piston return hinders the vent. In addition, the Entlüfteranschluß requires in the production of the slave cylinder a significant overhead, which is generally undesirable in the mass production of such cylinder.

PRESENTATION OF THE INVENTION

The invention has for its object to provide a simple as possible and compact hydraulic cylinder, in particular slave cylinder for a hydraulic clutch actuation for motor vehicles, which can be compared to the generic state of the art simpler way vented.

This object is achieved by the features specified in claim 1. According to the invention is in a hydraulic cylinder, in particular slave cylinder for a hydraulic clutch actuator for motor vehicles, which has a pressure chamber, on one side by a longitudinally displaceable in a cylinder housing piston, on the other side of a housing bottom of the cylinder housing and radially outward of a peripheral wall of the cylinder housing is limited, wherein the pressure chamber is optionally acted upon via a pressure in the housing bottom pressure port to move the piston in the cylinder housing, provided in the pressure chamber at the bottom of the housing insert, which is inserted into the pressure port and one with the pressure port communicating channel portion which extends in the installed position of the hydraulic cylinder in a substantially vertical direction and opens in the vicinity of the peripheral wall of the cylinder housing in the pressure chamber.

The simple inserted into the existing existing pressure port insert provides with its opening in an upper region of the pressure chamber channel section for a special rinsing effect in the pressure chamber, especially in the hydraulic relief of the hydraulic cylinder, ie during the piston return, which rinsing effect a continuous, automatic venting of the hydraulic cylinder Operation guaranteed. Special breather connections or the like. are dispensable, which alone leads to space advantages. Other effects and Advantages of the invention will become apparent from the detailed description of a preferred embodiment.

Advantageous or expedient refinements and developments of the invention are further subject matter of the claims 2 to 16 and are also described below.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1

eine Längsschnittansicht eines erfindungsgemäß ausgebildeten Nehmerzylinders für eine hydraulische Kupplungsbetätigung für Kraftfahrzeuge, mit einer in einem mit einer Laufhülse ausgekleideten Zylindergehäuse aufgenommenen Kolbenbaugruppe, wobei der Nehmerzylinder in seiner unbetätigten Grund- oder Ruhestellung nach Erstbetätigung des Nehmerzylinders gezeigt ist, in der eine Kolbenstange der Kolbenbaugruppe mit ihrem aus dem Zylindergehäuse herausragenden Ende betätigungswirksam an einem Kupplungshebel angreift, während ein Kolben der Kolbenbaugruppe von einem am Boden des Zylindergehäuses vorgesehenen Einsatzteil beabstandet ist,

Fig. 2

eine Längsschnittansicht eines Grundkörpers des Zylindergehäuses des Nehmerzylinders gemäß Fig. 1 ohne Anbauteile, insbesondere ohne die das Zylindergehäuse auskleidende Laufhülse,

Fig. 3

eine Vorderansicht des Grundkörpers des Zylindergehäuses gemäß Fig. 2 von links in Fig. 2,

Fig. 4

eine perspektivische Darstellung des bei dem Nehmerzylinder gemäß Fig. 1 am Boden des Zylindergehäuses vorgesehenen Einsatzteils von schräg vorne,

Fig. 5

eine Seitenansicht des Einsatzteils gemäß Fig. 4,

Fig. 6

eine Vorderansicht des Einsatzteils gemäß Fig. 4 von links in Fig. 5,

Fig. 7

eine Rückansicht des Einsatzteils gemäß Fig. 4 von rechts in Fig. 5,

Fig. 8

eine Längsschnittansicht des Einsatzteils gemäß Fig. 4 und

Fig. 9

eine vergrößerte Darstellung des Details IX in Fig. 8.

In the following the invention with reference to a preferred embodiment with reference to the accompanying, partially schematic drawings is explained in more detail, in which elastomeric parts are shown to simplify the illustration in the undeformed state. In the drawings show:

Fig. 1

a longitudinal sectional view of an inventively designed slave cylinder for a hydraulic clutch actuator for motor vehicles, with a housed in a barrel sleeve cylinder housing piston assembly, wherein the slave cylinder is shown in its unactuated basic or rest position after the first operation of the slave cylinder, in which a piston rod of the piston assembly with her operatively engaging a clutch lever from the cylinder housing, while a piston of the piston assembly is spaced from an insert provided at the bottom of the cylinder housing,

Fig. 2

a longitudinal sectional view of a main body of the cylinder housing of the slave cylinder according to Fig. 1 without add-on parts, in particular without the running sleeve lining the cylinder housing,

Fig. 3

a front view of the main body of the cylinder housing according to Fig. 2 from the left in Fig. 2 .

Fig. 4

a perspective view of the slave cylinder according to Fig. 1 at the bottom of the cylinder housing provided insert from diagonally forward,

Fig. 5

a side view of the insert according to Fig. 4 .

Fig. 6

a front view of the insert according to Fig. 4 from the left in Fig. 5 .

Fig. 7

a rear view of the insert according to Fig. 4 from the right in Fig. 5 .

Fig. 8

a longitudinal sectional view of the insert according to Fig. 4 and

Fig. 9

an enlarged view of detail IX in Fig. 8 ,

DETAILED DESCRIPTION OF AN EMBODIMENT

The Fig. 1 shows a slave cylinder 10 for a hydraulic clutch actuation for motor vehicles exemplarily for a hydraulic cylinder designed according to the invention. The slave cylinder 10 has a generally numbered 12 cylinder housing in which a piston assembly 14 is received longitudinally displaceable, which comprises a piston 16 and a at least tension and compression-resistant manner connected to the piston 16 piston rod 18. In the cylinder housing 12 is a pressure chamber 20 which is located on the in Fig. 1 left side variable from the piston 16, on the in Fig. 1 the right side of a housing bottom 22 of the cylinder housing 12 and radially outwardly fixed by a peripheral wall 24 of the cylinder housing 12 is limited. The pressure chamber 20 is optionally a provided on the housing bottom 22 pressure port 26, which is connected in the assembled state of the slave cylinder 10 in a conventional manner via a pressure line, not shown, to a clutch master cylinder, also not shown, acted upon by a pressure medium, such as brake fluid to move the piston 16 in the cylinder housing 12. Further, on the side facing away from the pressure chamber 20 side of the piston 16, a spring element in the form of a helical compression spring 28 is provided, which at its in Fig. 1 right end is supported on the cylinder housing 12 and with its in Fig. 1 engages the left end of the piston rod 18, so that the helical compression spring 28 biases the piston assembly 14 in a direction away from the housing bottom 22 direction to the piston rod 18 in the assembled state of the slave cylinder 10 in contact with a in Fig. 1 schematically drawn clutch lever 30 to hold. As will be described in more detail below, an insert 32 is provided in the pressure chamber 20 on the housing bottom 22, more precisely used in the pressure port 26 in the housing bottom 22, which advantageously performs several functions in the illustrated embodiment. On the one hand, the insert 32 serves as a fixing element which fixes the piston assembly 14 prior to a first actuation of the slave cylinder 10 in a predetermined stroke position with respect to the cylinder housing 12 and is adapted to release the piston assembly 14 with respect to the cylinder housing 12 with the first actuation of the slave cylinder 10 , wherein the insert part 32 for releasable fixing of the piston assembly 14 with respect to the cylinder housing 12 with a counter-element on the piston 16, here in the form of an extension 34, cooperates. On the other hand, the insert member 32 serves as a kind of deaerator for the pressure chamber 20, to which it has a communicating with the pressure port 26 channel portion 36 which extends in the in Fig. 1 shown installation position of the slave cylinder 10 extends substantially in the vertical direction and opens in the vicinity of the peripheral wall 24 of the cylinder housing 12 in the pressure chamber 20.

According to Fig. 1 For example, the cylinder housing 12 has a main body 38 which is preferably injection-molded from plastic and which is in Fig. 2 is shown separately. On the outer circumference of the base body 38 is provided with a mounting flange 40 for mounting the slave cylinder 10 in the motor vehicle having two mounting holes 42, which according to Fig. 1 are reinforced by means of slotted steel bushings 44. By the lined with the steel bushes 44 mounting holes 42 extend in the assembled state of the slave cylinder 10, for example screws (not shown) therethrough, which serve the attachment of the slave cylinder 10 at about a transmission wall (not shown) in the vehicle. In the Fig. 1 and 2 To the left of the mounting flange 40, the base body 38 of the cylinder housing 12 of the further outer peripheral side has a radial groove 46, in accordance with Fig. 1 an elastomeric protective cap 50 having a bellows portion 48 surrounding the piston rod 18 is knotted with an inner peripheral annular collar 52.

On the inner peripheral side, the main body 38 of the cylinder housing 12 has an in Fig. 2 to the left, stepped bore 54, in accordance with Fig. 1 a preferably metallic sleeve 56 is used as a further component of the cylinder housing 12. The sleeve 56 has two hollow cylindrical sleeve portions 58, 60 of different diameters, which are connected to each other at the bottom 22 of the cylinder housing 12 via a ring portion 62. Starting from the in Fig. 2 left side, the bore 54 of the body 38 now has four sections 64, 66, 68 and 70 of different diameters, which in the Fig. 1 and 2 scaled down from left to right.

The first bore portion 64 has at its open end an undercut 72 which serves to define an annular, slotted for mounting securing element 74 preferably made of plastic on the cylinder housing 12, which at the in Fig. 1 left end face of the sleeve 56 abuts and thus the Running sleeve 56 in the main body 38 of the cylinder housing 12 secures. In the second bore portion 66 of the stepped bore 54 of the base body 38 of the larger diameter sleeve portion 58 of the barrel sleeve 56 is tightly received, which forms the pressure chamber 20 bounding peripheral wall 24 with its inner peripheral surface. The third bore section 68 adjoins the second bore section 66 via an annular shoulder 76 against which the annular section 62 of the running sleeve 56 abuts. In the third bore section 68 of the stepped bore 54 in the base body 38 of the smaller diameter sleeve portion 60 of the barrel sleeve 56 is tightly received. In this case, the sleeve portion 60 is provided on the outer peripheral side with a radial groove 78 for receiving an O-ring 80, which provides a static seal between the third bore portion 68 and the sleeve portion 60. At the third bore portion 68 is followed by a further annular shoulder 82 of the fourth bore portion 70, wherein the dimensions of the smaller diameter sleeve portion 60 of the sleeve 56 on the one hand and the third and fourth bore portions 68, 70 of the stepped bore 54 on the other hand are coordinated so that a annular end face 84 of the sleeve portion 60 has a small axial distance from the annular shoulder 82 and projects beyond this for mounting the insert 32 described in more detail below in the pressure port 26 radially inwardly. Like the other FIGS. 2 and 3 can be seen, the fourth bore portion 70 of the stepped bore 54 in the body 38 is provided on the inner peripheral side with a plurality of, in the illustrated embodiment, four in the axial direction of the cylinder housing 12 extending longitudinal ribs 86 which protrude radially inwardly, unevenly or asymmetrically over the Scope of the fourth bore portion 70 are distributed and serve a rotational angle orientation of the insert member 32 in the pressure port 26, as will also be explained in more detail below. At the in the Fig. 1 and 2 The right end of the fourth bore section 70 finally opens a formed in the base body 38, smaller diameter pressure port bore 88 in the fourth bore portion 70th

Although in the illustrated embodiment, the fourth bore portion 70 of the stepped bore 54 has a smaller diameter than the third bore portion 68, so that the base body 38 of the cylinder housing 12 in this area substantially following the outer contour of the base body 38 does not have excessively large differences in wall thickness, If the outer contour of the main body 38 is changed, the fourth bore section 70 could in principle also be formed with a diameter which corresponds to the diameter of the third bore section 68.

From the above description, it can be seen that the pressure port bore 88, the fourth bore portion 70 of the stepped bore 54 and the sleeve portion 60 of the barrel 56 accommodated in the third bore portion 68 are part of the pressure port 26, via which the pressure chamber 20 can be acted upon by the pressure medium , As a result of the effect caused by the O-ring 80 static seal on the outer circumference of the smaller diameter sleeve portion 60 of the barrel 56 this undergoes pressurization of the pressure chamber 20 via the pressure port 26, wherein the hydraulic pressure on the annular end face 84 of the sleeve portion 60 and the on the other side of this area larger, the pressure chamber 20 facing end face of the annular portion 62 of the barrel sleeve 56 acts, a resultant force to the right in Fig. 1 , which endeavors to keep the running sleeve 56 in the stepped bore 54 of the base body 38, so relieves the attachment of the running sleeve 56 in the base body 38 by means of the securing element 74.

Again Fig. 1 it can be seen further, the one with a small radial clearance in the larger diameter sleeve portion 58th the running sleeve 56 of the cylinder housing 12 guided, in the illustrated embodiment metallic piston 16 on the outer circumference of a radial groove 90 for receiving a Nutrings 92. The elastomeric groove ring 92 is in a conventional manner with its outer peripheral side sealing lip under a certain bias on the peripheral wall 24 of the cylinder housing 12 and thus ensures a dynamic seal of the pressure chamber 20 to the left in Fig. 1 ,

On the in Fig. 1 left side of the piston 16 is further provided with a central recess 94 in which a on in Fig. 1 right end of the piston rod 18 formed ball head 96 is held by means of a securing element 98 hinged, so that the piston rod 18 with respect to the piston 16 has a certain angular mobility. Instead of in Fig. 1 shown embodiment of the piston assembly 14, this could also be integrally formed, with a piston rod conically or spherically sloping down piston outer surface to ensure the angular mobility, as it is in principle from the DE 43 22 969 A1 or the DE 43 31 241 A1 is known.

The metallic piston rod 18 in the illustrated embodiment has on the in Fig. 1 left side a thickened end 100 having a substantially spherical end surface 102, via which the piston rod 18 operatively acts on the clutch lever 30. At the entrance of the thickened end 100, the piston rod 18 further comprises a collar 104, which serves to connect the protective cap 50 to the piston rod 18, wherein the annular collar 104 of the piston rod 18 positively in a substantially complementary shaped annular recess 106 in a mounting portion 108 of Protective cap 50 engages, which adjoins the bellows portion 48 of the protective cap 50 on the side facing away from the pressure chamber 20 side of the protective cap 50. On the other hand, the annular collar 104 of the piston rod 18 with its the pressure chamber 20 facing end face an abutment for the helical compression spring 28, wherein from the annular collar 104 facing the end of the helical compression spring 28 and a certain radial centering for the piston rod 18 emanates, which is advantageous in the assembly of the slave cylinder 10 in the vehicle.

Of the Fig. 1 It can also be seen that the securing element 74 is provided for holding the sleeve 56 in the cylinder housing 12 on its side facing away from the pressure chamber 20 side with an axial groove 110, which faces as a further abutment and centering of the pressure chamber 20, in Fig. 1 right end of the helical compression spring 28 is used, which widens in diameter, starting from the annular collar 104 to the axial groove 110 toward substantially conical, so it is frusto-conical. By this displacement of the helical compression spring 28 from the pressure chamber 20 and the sleeve 56 toward the position shown between fuse element 74 and collar 104 on the piston rod 18, compared to the above-described prior art, advantageously the ratio of stroke to dead space volume (or actual volume be reduced in the illustrated basic position of the piston 16) of the pressure chamber 20, which ultimately allows a shortening of the axial length of the cylinder housing 12. In addition, again compared with the initially discussed prior art, the pressure chamber 20 is better flushed or emptied of the pressure medium at a return of the piston 16 from an actuating position to its normal position, which contributes to a better ventilation of the slave cylinder 10. This also eliminates the previously known piston return spring in the pressure chamber as a crystallization of air bubbles.

The FIGS. 4 to 9 Now further details of the preferably molded from a plastic, such as polyamide 66 with a glass fiber reinforcement insert 32 can be seen, according to particular Fig. 8 is formed in all its areas with a substantially constant wall thickness to form distortions and thus to avoid insufficient dimensional stability due to accumulation of material.

The insert 32 is based on a flat base plate 112 with plane-parallel end faces, of which the in Fig. 5 right end face in the mounted state of the insert member 32 is flat against the pressure chamber 20 facing end face of the annular portion 62 of the barrel 56 abuts. On the base plate 112, three functional portions of the insert member 32 are arranged, namely on the side remote from the pressure chamber 20 side of the base plate 112, a mounting portion 114 for attachment of the insert 32 in the pressure port 26, on the pressure chamber 20 side facing the base plate 112 a tether portion 116 to releasably Fixation of the piston assembly 14 with respect to the cylinder housing 12 and, also on the side facing the pressure chamber 20 side of the base plate 112, the channel description already mentioned at the beginning of the description of the figures for venting the pressure chamber 20th

In the illustrated embodiment, the insert member 32 is mounted by means of a snap connection in the pressure port 26. For this purpose, the substantially hollow cylindrical mounting portion 114 is provided at its side facing away from the base plate 112, the free end outer peripheral side with a segmented annular collar 118, the base plate 112 facing end face forms a substantially annular, segmented abutment surface 120. Starting from its free end, the fastening portion 114 of the further to form spring arms 122 a plurality of, in the illustrated embodiment, four in the longitudinal direction of the mounting portion 114 extending slots 124 whose asymmetrical distribution over the circumference of the mounting portion 114 (see Fig. 7 ) of the distribution of the longitudinal ribs 86 in the fourth bore portion 70 of the stepped bore 54 in the main body 38 of the cylinder housing 12 (see FIG. Fig. 3 ) corresponds. Here are the slots 124 in the mounting portion 114 of the insert member 32 on the one hand and the longitudinal ribs 86 in the base body 38 of the cylinder housing 12 on the other hand dimensionally matched to one another that engage in the mounted state of the insert member 32, the longitudinal ribs 86 with a small circumferential clearance in the slots 124, but not radially inwardly over the spring arms 122 protrude. The asymmetrical, coordinated circumferential distribution of the longitudinal ribs 86 / slots 124 provides a simple way for a clear rotational angle orientation of the mounted insert 32 in the slave cylinder 10, namely such that the channel portion 36 is aligned on the insert member 32 in a vertical upward direction, as in Fig. 1 shown. In the assembled state of the insert part 32 this is positively fixed in the slave cylinder 10 in the axial direction, wherein the abutment surface 120 on the annular collar 118 of the mounting portion 114 in accordance Fig. 1 the over the fourth bore portion 70 of the stepped bore 54 in the body 38 radially inwardly projecting, annular end face 84 of the smaller diameter sleeve portion 60 of the barrel 56 in the cylinder housing 12 engages snap-hook like.

For preferably automated production of the above-described snap connection between the cylinder housing 12 and with respect to the cylinder housing 12 angle-oriented insert 32, the latter is inserted starting from the open end of the barrel sleeve 56 lined cylinder housing 12 in the barrel 56 to the spring arms 122 of the mounting portion 114 at a small slope between the ring portion 62 and the inner circumference of the smaller diameter sleeve portion 60 of the sleeve 56 come to rest. In the further axial relative displacement of the insert member 32 with respect to the cylinder housing 12, the spring arms 122 spring radially inward. As a result, the longitudinal ribs 86 thread in the fourth bore portion 70 of the main body 38 of the cylinder housing 12 in the slots 124 of the attachment portion 114th of the insert 32 before the spring arms 122 rebound radially outward again and latch with their segmented abutment surface 120 behind the annular end face 84 of the sleeve portion 60. At substantially the same time, the base plate 112 of the insert 32 comes with its the pressure port 26 facing end side of the pressure chamber 20 facing end face of the annular portion 62 of the barrel 56 to the plant. Since both the transition from the pressure port 26 facing end face of the spring arms 122 to the outer peripheral surface and the transition of the pressure chamber 20 facing end face of the longitudinal ribs 86 to the inner peripheral surface at right angles, only with a broken edge, ie without slope, can be that Insert part 32 to the cylinder housing 12 only with correct angular orientation of these parts to each other. In an attempt to add an incorrectly or incorrectly oriented insert 32 to the cylinder housing 12, the facing end surfaces on the spring arms 122 on the one hand and the longitudinal ribs 86 on the other hand substantially flat against each other and thus prevent further axial displacement of the insert 32 with respect to the cylinder housing 12th Since, moreover, the angular orientation of the insert 32 with respect to the cylinder housing 12 takes place on the base body 38, a circumferential fixing of the running sleeve 56 in the base body 38 is not required.

Like the other Fig. 1 . 7 and 8 can be seen, limited the mounting portion 114 on the inner peripheral side a cylindrical, aligned with the central axis M of the slave cylinder 10 channel portion 126 which passes through the base plate 112 of the insert 32. On the pressure chamber 20 side facing the base plate 112, the channel sections 36 and 126 intersect, so that a substantially rectangular passage between the pressure chamber 20 and the pressure port 26 is. As the Fig. 1 shows, the vertical ending ends Channel section 36 just before the peripheral wall 24 of the cylinder housing 12 in the pressure chamber 20th

Now, any air pockets or bubbles collect in the pressure medium 20 located in the pressure medium above the pressure chamber 20. Similarly, heated hydraulic fluid in the pressure chamber 20 rises upwards in the pressure chamber 20. In a return of the piston 16 from an actuating position in his in Fig. 1 illustrated basic position, there is a directional forced flow through the channel sections 36 and 126 via the pressure port 26 and the pressure line, not shown, to the clutch master cylinder, also not shown, which in turn is connected to a reservoir, not shown, as already mentioned. As a result of the opening of the channel section 36 to a region located in the pressure chamber 20 above the accumulated air pockets or bubbles are entrained there as well as the ascended there, heated hydraulic fluid from the forced flow and thus discharged from the slave cylinder 10. Accordingly, the insert 32 provides with its vertically extending channel portion 36 for a continuous and safe self-venting of the slave cylinder 10 and a discharge of heated hydraulic fluid, which additional breather connections or the like. dispensable.

Finally, the tether portion 116 of the insert 32 has a fitting to the base plate 112, in the assembled state of the insert 32 according to Fig. 1 with the central axis M of the slave cylinder 10 axially aligned hollow cylinder 128, according to the Fig. 1 and 8th is broken laterally from the channel section 36. At its end facing the piston 16 of the hollow cylinder 128 is provided on the inner peripheral side with a circumferential, radially inwardly projecting annular bead 130 which in Fig. 9 is shown enlarged and the temporary, positive bondage of the piston 16 and thus the piston assembly 14 on the insert 32 is used. For this purpose, the torus acts 130 with the pressure chamber-side extension 34 of the piston 16, more precisely with an end remote from the piston 16 of the extension 34 on the outer peripheral side integrally formed annular collar 132 (FIG. Fig. 1 ), which has a slightly tapered to the pressure port 26 outer surface. The according to Fig. 9 to the pressure chamber 20 towards rounded annular bead 130 on the tether portion 116 of the insert part 32 on the one hand and the collar 132 on the extension 34 of the piston 16 on the other hand are dimensionally coordinated such that the inside diameter of the annular ring 130 is slightly smaller than the largest outer diameter of the annular collar 132, while whose distance from the end face of the piston 16 is slightly greater than the axial length of the annular bead 130th

To bind the piston assembly 14 on the insert member 32 during assembly of the slave cylinder 10, the piston assembly 14 against the force of the helical compression spring 28 as far as in the sense of reducing the pressure chamber 20 into the cylinder housing 12 pushed into the extension 34 on the piston 16 with its insert 32 towards beveled annular collar 132 on which the pressure chamber 20 facing, rounded annular bead 130 comes to rest. In a further axial relative displacement of the piston assembly 14 with respect to the cylinder housing 12 in the direction of the pressure port 26 of the annular collar 132 extends on the piston extension 34, the annular bead 130 of the tether portion 116 elastically radially outward. After overpressure of the annular bead 130 this snaps due to the elastic properties of the material of the insert member 32 behind the annular collar 132, ie in the annular gap between the annular collar 132 and the pressure chamber 20 facing end face of the piston 16 a. The piston assembly 14 is now positively fixed to the tether portion 116 of the insert 32.

Thus, since the piston assembly 14 is tied in a position in which they as far as possible in the cylinder housing 12th pushed in, the slave cylinder 10 required during storage, transport and installation in the vehicle only a small space. In addition, the slave cylinder 10 can be mounted substantially force-free in the vehicle, because the helical compression spring 28 does not have to be compressed, but is held by means of the insert 32 caused binding of the piston assembly 14 in a biased position. This also allows an assembly of the slave cylinder 10 in the motor vehicle as part of a hydraulic clutch actuation, as pre-assembled from master cylinder, expansion tank, pressure line and slave cylinder 10 and with hydraulic fluid (part) prefilled unit is supplied to the assembly line of the motor vehicle manufacturer, wherein the filling volume of the slave cylinder 10th in the tethered position of the piston assembly 14 almost the idle volume of the operating slave cylinder 10 in the in Fig. 1 shown basic position of the piston assembly 14 corresponds.

For the first actuation of the slave cylinder 10 mounted in the motor vehicle, the pressure medium is supplied via the pressure connection 26 to the pressure chamber 20. As a result of this in the pressure chamber 20 building pressure acting on the active surface of the piston 16, the piston 16 undergoes an in Fig. 1 to the left directed force, which adds up to the force of the helical compression spring 28. If the sum of these forces exceeds the holding force of the connection between the projection 34 of the piston 16 and the tether portion 116 of the insert 32, the annular bead 130 on the tether portion 116 is widened again via the annular collar 132 on the extension 34, whereupon the piston assembly 14 is released from the insert 32. A further binding of the piston assembly 14 during operation of the slave cylinder 10 is not provided and can not be done because of in Fig. 1 shown distance between the extension 34 on the piston 16 and the tether portion 116 on the insert part 32 during operation of the slave cylinder 10 is no longer undershot.

From the above description it is seen that the holding force of the connection between the extension 34 of the piston 16 and the tether portion 116 of the insert member 32 is designed constructively such that it is on the one hand sufficiently larger than the spring force of the helical compression spring 28 to unintentional release of the bondage the piston assembly 14 to prevent, on the other hand, but sufficiently smaller than the holding force of the connection between the insert member 32 and the cylinder housing 12 so that the insert member 32 is not pulled out of the pressure port 26 at the first actuation of the slave cylinder 10.

Although the tether portion 116 is provided in the embodiment described above on the inner peripheral side with a circumferentially closed contour in the form of the annular bead 130 which cooperates with the collar 132 on the extension 34 of the piston 16 as described, the piston assembly 14 in the manner of a snap connection temporarily on To bind insert 32, this positive connection can also be configured differently, such as with spring arms and snap hook thereon as a shackle portion of the insert, analogous to the above-described determination of the insert in the pressure port.

It is disclosed a hydraulic cylinder having a pressure chamber which is delimited on one side by a longitudinally displaceable in a cylinder housing piston, on the other side of a housing bottom of the cylinder housing and radially outwardly from a peripheral wall of the cylinder housing, wherein the pressure chamber optionally can be acted upon by a provided on the housing bottom pressure port with a pressure medium to move the piston in the cylinder housing. According to the invention, an insert part is used in the pressure connection, which has a communicating with the pressure port channel portion which extends in the installed position of the hydraulic cylinder in a substantially vertical direction and opens in the vicinity of the peripheral wall of the cylinder housing in the pressure chamber. As a result, a simple and compact hydraulic cylinder is provided, which can be vented in a simpler manner compared to the prior art.

LIST OF REFERENCE NUMBERS

10

slave cylinder

12

cylinder housing

14

piston assembly

16

piston

18

piston rod

20

pressure chamber

22

caseback

24

peripheral wall

26

pressure connection

28

Helical compression spring

30

clutch lever

32

insert

34

extension

36

channel section

38

body

40

mounting flange

42

mounting hole

44

steel bushing

46

radial groove

48

bellows

50

protective cap

52

collar

54

stepped bore

56

running sleeve

58

sleeve section

60

sleeve section

62

ring section

64

first bore section

66

second bore section

68

third bore section

70

fourth bore section

72

undercut

74

fuse element

76

annular shoulder

78

radial groove

80

O-ring

82

annular shoulder

84

annular end face

86

longitudinal rib

88

Pressure connecting bore

90

radial groove

92

Nutring

94

recess

96

ball head

98

fuse element

100

The End

102

end face

104

collar

106

ring recess

108

attachment section

110

axial groove

112

baseplate

114

attachment section

116

holding section

118

collar

120

Abutment surface

122

spring arm

124

slot

126

channel section

128

hollow cylinder

130

torus

132

collar

M

central axis

Claims (16)

1. Hydraulic cylinder (10), in particular slave cylinder for a hydraulic clutch actuation system for motor vehicles, with a pressure chamber (20) which is delimited on one side by a piston (16) accommodated in a longitudinally displaceable manner in a cylinder housing (12), on the other side by a housing bottom (22) of the cylinder housing (12), and radially outwards by a circumferential wall (24) of the cylinder housing (12), wherein the pressure chamber (20) can selectively be acted upon by a pressure medium via a pressure connection (26) provided in the housing bottom (22) in order to displace the piston (16) in the cylinder housing (12), characterized in that an insertion part (32) is provided in the pressure chamber (20) at the housing bottom (22), the insertion part being inserted in the pressure connection (26) and comprising a channel section (36) which communicates with the pressure connection (26) and, in the installed position of the hydraulic cylinder (10), extends essentially in the vertical direction and opens into the pressure chamber (20) in the vicinity of the circumferential wall (24) of the cylinder housing (12).
2. Hydraulic cylinder (10) according to Claim 1, characterized in that the cylinder housing (12) has a basic body (38) made of plastic, which basic body is provided with a bore (54) in which a metallic sleeve (56) for the piston (16) is inserted.
3. Hydraulic cylinder (10) according to Claim 2, characterized in that the sleeve (56) comprises two sleeve sections (58, 60) of different diameter which are joined to one another at the housing bottom (22) of the cylinder housing (12) via an annular section (62) which together with a circumferential wall (24) of the larger-diameter sleeve section (58) delimits the pressure chamber (20), wherein the sleeve (56) is sealed relative to the basic body (38) of the cylinder housing (12) against the pressure in the pressure chamber (20) by means of a static seal (80) which is seated between the smaller-diameter sleeve section (60) of the sleeve (56) and a bore section (68) of the stepped bore (54) in the basic body (38) which is assigned thereto.
4. Hydraulic cylinder (10) according to any of the preceding claims, characterized by a spring element (28) which prestresses the piston (16) in a direction away from the housing bottom (22) and is arranged on the side of the piston (16) facing away from the pressure chamber (20).
5. Hydraulic cylinder according to Claim 2 or 3 and Claim 4, characterized in that the sleeve (56) is secured in the basic body (38) of the cylinder housing (12) by means of an annular securing element (74) which is passed through by a piston rod (18) that is connected to the piston (16) at least in manner resistant to tension and pressure, said securing element forming, on its side facing away from the pressure chamber (20), an abutment (110) for one end of the spring element (28), the other end of said spring element being supported against an annular collar (104) on the piston rod (18).
6. Hydraulic cylinder (10) according to any of the preceding claims, characterized in that the insertion part (32) is anchored axially in the pressure connection (26) in a form-fitting manner.
7. Hydraulic cylinder (10) according to Claim 6, characterized in that the insertion part (32) is anchored in the pressure connection (26) by means of a snap connection.
8. Hydraulic cylinder (10) according to Claim 7, characterized in that the insertion part (32) has, on its side facing away from the pressure chamber (20), a hollow-cylindrical fixing section (114) which is provided with an annular collar (118) on its outer circumference and, starting from its free end, has multiple longitudinal slots so as to form a plurality of resilient arms (122), wherein the annular collar (118) on the fixing section (114), in the mounted state of the insertion part (32), engages behind an annular end face (84) in the pressure connection (26), said annular end face facing away from the pressure chamber (20).
9. Hydraulic cylinder (10) according to at least Claims 2 and 8, characterized in that the annular end face (84) in the pressure connection (26) which is engaged behind by the insertion part (32) is formed by the sleeve (56) of the cylinder housing (12).
10. Hydraulic cylinder (10) according to any of the preceding claims, characterized in that the channel section (36) of the insertion part (32) is hydraulically connected to a hollow-cylindrical fixing section (114) which is plugged into the pressure connection (26) at the housing bottom (22) of the cylinder housing (12).
11. Hydraulic cylinder (10) according to Claim 10, characterized in that the insertion part (32) is anchored in the pressure connection (26) at an oriented angle of rotation relative to the cylinder housing (12) and in a form-fitting manner in the circumferential direction.
12. Hydraulic cylinder (10) according to Claim 11, characterized in that the hollow-cylindrical fixing section (114) of the insertion part (32) is provided with at least two longitudinal slots (124) which are distributed asymmetrically over the circumference of the fixing section (114), whereas the pressure connection (26) is provided with at least two longitudinal ribs (86) on its inner circumference, the distribution of said longitudinal ribs over the circumference of the pressure connection (26) corresponding to the distribution of the longitudinal slots (124) in the insertion part (32), wherein, in the mounted state of the insertion part (32), the longitudinal ribs (86) on the pressure connection (26) engage in the longitudinal slots (124) in the insertion part (32) in such a way as to orient the angle of rotation.
13. Hydraulic cylinder (10) according to any of the preceding claims, characterized by a fixing element which fixes the piston (16) in a predefined stroke position relative to the cylinder housing (12) prior to first actuation of the hydraulic cylinder (10) and is designed to release the piston (16) relative to the cylinder housing (12) upon first actuation of the hydraulic cylinder (10), wherein the insertion part (32) likewise forms the fixing element and cooperates with a mating element (34) on the piston (16) to releasably fix the piston (16) relative to the cylinder housing (12).
14. Hydraulic cylinder (10) according to Claim 13, characterized in that the insertion part (32) has a holding section (116) to which an extension (34) on the pressure chamber side can be fixed in a form-fitting manner, said extension (34) forming the mating element on the piston (16).
15. Hydraulic cylinder (10) according to Claim 14, characterized in that the holding section (116) of the insertion part (32) comprises a hollow cylinder (128) which is aligned axially relative to a central axis (M) of the pressure chamber (20) and has an annular bead (130) on its inner circumference, whereas the centric extension (34) on the piston (16) is provided with an annular collar (132) on its outer circumference, which annular collar engages behind the annular bead (130) in the condition where the piston (16) is fixed to the insertion part (32).
16. Hydraulic cylinder (10) according to any of the preceding claims, characterized in that the insertion part (32) is injection-molded from a plastic.

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